US20080148893A1 - Collar Having End-Side Teeth For a Drivable Wheel Hub - Google Patents
Collar Having End-Side Teeth For a Drivable Wheel Hub Download PDFInfo
- Publication number
- US20080148893A1 US20080148893A1 US11/910,803 US91080306A US2008148893A1 US 20080148893 A1 US20080148893 A1 US 20080148893A1 US 91080306 A US91080306 A US 91080306A US 2008148893 A1 US2008148893 A1 US 2008148893A1
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- United States
- Prior art keywords
- collar
- hub
- contour
- rotational axis
- radially
- Prior art date
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- Granted
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C43/00—Assembling bearings
- F16C43/04—Assembling rolling-contact bearings
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
- B60B27/00—Hubs
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
- B60B27/00—Hubs
- B60B27/0005—Hubs with ball bearings
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
- B60B27/00—Hubs
- B60B27/0015—Hubs for driven wheels
- B60B27/0021—Hubs for driven wheels characterised by torque transmission means from drive axle
- B60B27/0031—Hubs for driven wheels characterised by torque transmission means from drive axle of the axial type, e.g. front teeth
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
- B60B27/00—Hubs
- B60B27/0078—Hubs characterised by the fixation of bearings
- B60B27/0084—Hubs characterised by the fixation of bearings caulking to fix inner race
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
- B60B27/00—Hubs
- B60B27/0094—Hubs one or more of the bearing races are formed by the hub
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
- F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
- F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
- F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
- F16C19/186—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with three raceways provided integrally on parts other than race rings, e.g. third generation hubs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
- F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
- F16C35/063—Fixing them on the shaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
- F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
- F16D1/064—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end non-disconnectable
- F16D1/072—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end non-disconnectable involving plastic deformation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
- F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
- F16D1/076—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end by clamping together two faces perpendicular to the axis of rotation, e.g. with bolted flanges
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2326/00—Articles relating to transporting
- F16C2326/01—Parts of vehicles in general
- F16C2326/02—Wheel hubs or castors
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/1987—Rotary bodies
Definitions
- the invention relates to a collar made from cold plastically shaped material of a hub, with which at least one inner ring of a wheel bearing unit is secured axially in a fixed manner on the hub and in which teeth for engagement in a mating toothing are formed at the end.
- the wheel bearing unit generally an angular ball bearing arrangement or angular roller arrangement, is held free of play in a prestressed fashion by means of the collar.
- the finished collar 3 according to FIG. 1 is, as illustrated in FIG. 2 a and FIG. 3 , shaped from a hollow end piece 2 which is formed in one piece with a hub 1 .
- the material of the end piece 2 is turned-over plastically over the edge 4 of the inner ring 5 radially toward the outside. If the collar 3 , as also illustrated in FIG.
- the teeth 7 are either also formed when the end piece 2 is placed around to form the collar 3 or the teeth 7 are formed in the finished collar 3 with a separate method step.
- the mating toothing is formed, for example, on a bell of a cardan shaft.
- the collar 3 is shaped with a tool from the end piece 2 .
- the end piece 2 which is initially essentially hollow-cylindrical, as illustrated in FIG. 3 , is widened in a radial funnel shape and is shaped in the end position according to FIG. 2 b to form the collar 3 .
- the formation of the teeth 7 is problematic.
- the material of the part 8 of the end piece 2 tapers during the widening and turning-over process and flows radially outward.
- the respective tooth 7 is not fully formed toward the outside owing to the uncontrollable flowing away of the material, and the loadbearing component, which is determined in particular by the dimension B, is small.
- B is a line segment between the points S and T.
- the component C and A ⁇ (B+C) which is not filled in here is small measured in terms of the overall proportion of the tooth 7 over the length A.
- the edges of all the teeth of the end toothing engage with both edges of all the teeth of the mating toothing.
- the toothings are braced axially by means of one or more screw elements. Torques are transmitted to the wheel hub by the frictional engagement/positive engagement generated by surface pressure.
- connection of the articulated part to a wheel hub is advantageous in particular if high torques are to be transmitted from the drive to the wheel or, under certain circumstances, also in the reversed torque flow.
- the possibilities in terms of installation space and thus in terms of the rigidity of the pairs of inner toothings and outer toothings which are generally used are often already exploited to the full so that the end toothing is, compared to the latter, a reliable alternative which provides a saving in terms of installation space.
- the rigid configuration for transmitting high torques to the wheel can have a disadvantageous effect if, in the case of overloading, a fracture in the wheel hub leads to loss of the vehicle wheel in the most unfavorable case.
- the object of the invention is therefore to provide a collar with whose design the previously mentioned disadvantages are avoided.
- the collar is formed from plastically shaped material of the end piece of the hub.
- the material of the hollow end piece is preferably shaped cold by what is referred to as rolling riveting, a process of widening, bending and stamping, radially outward over the radially inner and axially outer edge of the inner ring.
- the end piece which is formed in one piece with the hub is, according to the invention, not essentially hollow-cylindrical but rather has an accumulation of material.
- the accumulation of material is formed at the part of the end piece which protrudes axially beyond the inner edge of the inner ring. Owing to the rotational symmetry of the end piece, the accumulation of material which runs around the rotational axis is generally a bead-shaped thickened portion which is continuous or interrupted in the circumferential direction.
- the thickened portion is designed in any desired way and can protrude in both radial directions, that is to say radially outward away from the rotational axis and/or toward the rotational axis.
- the thickened portion preferably protrudes out of the end piece radially inward in the direction of the rotational axis of the hub before the collar is formed.
- One embodiment of the invention provides for the thickened portion to be formed on a free, axial end of the end piece which projects from the hub.
- the configuration of the individual tooth can be influenced and optimized by the shape and cross section of the thickened portion. There is thus provision for the outer contour of the thickened portion to drop away toward the end side of the end piece in the direction of the rotational axis.
- the contour of the teeth is represented partially as a line segment in respective sections through the collar which extend through the tooth head along the rotational axis, with the line segment delineating the respective tooth head at the end.
- the line segment describes the straight profile of the tooth head contour in the longitudinal section along the rotational axis.
- the optimum size of the line segment is provided with configurations of the invention.
- the shortest radial distance between the end points of the line segment is at least of precisely the same size, when viewed in an axial projection of the line segment, as half of the largest of this length of the respective tooth in the radial direction when viewed in an axial projection of the length of the tooth.
- Such a minimum amount ensures that each individual loadbearing tooth is filled in the axial direction and in the circumferential direction.
- the contour of the individual loadbearing tooth is initially described by a run-in contour in a longitudinal section along the rotational axis of the hub, with the run-in contour extending radially from the tooth base outward to the line segment rising over the rotational axis.
- the run-in contour is curved with any desired degree of concavity or convexity or is a chamfer.
- the run-in contour merges with the line segment at the radially inner end point of the end points.
- the line segment merges at the radially outer end point of the line segment with a run-out contour toward the tooth base, with the run-out contour extending from the end point rising progressively or degressively or linearly or in any other desired way over the rotational axis.
- the run-in contour and the run-out contour each end at the tooth base side at a sectional point at which the tooth merges with the hub.
- the sectional point is the root of the tooth at which the contour of the individual tooth merges with the solid base of the collar at the apex of the gap with the respective tooth.
- the distance between the radially outer end point at the end of the line segment and the radially outer sectional point of the sectional points is at maximum as large, in the axial projection, as a third of the maximum length of the respective tooth in the radial direction when considered in an axial projection.
- the length of the respective tooth is described by the distance between the sectional points.
- the teeth are of wedge-shaped design such that the geometric lines of the end toothing meet centrally at a common point on the rotational axis.
- the geometric lines are the body edges of the tooth excluding any edge radii, chamfers, rounded portions etc.
- a further embodiment of the invention provides for the edges of the teeth of the end toothing which are provided for engagement to be each inclined at an edge angle greater than 20° and less than 30°.
- the edge angle is half the tooth angle in the case of a symmetrically formed toothing.
- the edges are inclined with the edge angle with respect to a virtual pitch plane E which starts from the rotational axis.
- the diameter of the reference circle (median circumference of the end toothing about the rotational axis) of the toothing is accordingly generally prescribed within very tight limits. Accordingly, the behavior of the toothing, for example with respect to loads from the drive torques, can hardly be influenced, or cannot be influenced, by changes to the reference circle of the toothing.
- the geometry of the individual teeth of the toothing is influenced by means of the edge angle in such a way that an optimum number of teeth on a predefined circumference can be specified in terms of assembly and in terms of the loads from torques.
- the edge angle of the effective edges which are in play-free engagement with the mating toothing is preferably 22.5°.
- FIGS. 1 to 6 show longitudinal sections or details of longitudinal sections along the rotational axis 1 a of a wheel bearing arrangement 9 in various modifications of exemplary embodiments of the invention.
- FIGS. 1 , 3 , 5 show a wheel bearing arrangement 9 with a hub 1 , two rows of rolling bodies 10 and a vehicle flange 11 .
- the hub 1 has a flange 12 for attaching a vehicle wheel (not illustrated) and is mounted by means of the rolling bodies 10 so as to be rotatable about the rotational axis 1 a with respect to the vehicle flange 11 which is fixed to the vehicle.
- An inner ring 5 sits on the hub 1 and has a row of the rolling bodies 10 running on it.
- the end piece 14 , 15 or 17 which is connected in one piece to the hub 1 is in the initial position before the rolling riveting.
- the inner ring 5 is, as illustrated in an enlarged detail according to FIG.
- the hollow end piece 14 , 15 or 17 is shaped radially outward over an edge 4 of the inner ring 5 .
- the angular ball bearing arrangement is prestressed by means of the collar 16 .
- An end toothing 13 is formed in the collar 16 .
- the hollow end pieces 14 , 15 or 17 point in the axial direction in the initial state before the collar 16 is formed, and in the process they project axially beyond the edge 4 which is rounded with a radius R.
- the end pieces 14 , 15 or 17 have an accumulation of the material in the form of a radial thickened portion 18 , 19 or 20 at least at the part 8 at which they protrude axially beyond the edge 4 .
- the rotationally symmetrical thickened portion 18 (illustrated in FIG. 4 ) on the end piece 14 has the largest radial dimension X in the center and protrudes radially in the direction of the rotational axis 1 a and radially outward from the end piece 14 .
- the material is distributed in both radial directions.
- the thickened portion 19 which is illustrated in FIG. 5 protrudes radially in the direction of the rotational axis 1 a and is thickest at the free end of the end piece 15 which points in the axial direction.
- such an accumulation of material is effective in particular in the region C ( FIG. 6 ) so that less material flows outward and is thus available to fill in the cavities in the teeth 7 in the region B.
- the thickened portion 20 illustrated in FIG. 6 a protrudes radially in the direction of the rotational axis 1 a .
- the outer contour 29 of the thickened portion 20 drops away toward the end side 21 of the end piece 17 in the direction of the rotational axis 1 a .
- FIGS. 7 a and 7 b show the overall view of a possible configuration of the end toothing 13 in a highly simplified form.
- the teeth 7 are adjacent to one another at the circumference about the rotational axis 1 a and oriented radially along the length A.
- FIGS. 7 a and 7 b show how the geometry is described without rounding of the individual teeth 7 , formed in a wedge shape, at the head, base and edge side by radially oriented geometric lines 21 , 22 , 23 which meet at the sectional point P.
- the sectional point P is the common sectional point for all the geometric lines 21 , 22 , 23 of the crown gear which extend radially.
- the tooth angle ⁇ between the edges 30 is twice the tooth edge angle ⁇ and is constant over the entire radial extent of each individual tooth 7 .
- the contour of the teeth 7 is represented in respective sections, extending through the tooth head 25 along the rotational axis 1 a , through the collar 16 as a line segment 24 , with the line segment 24 delineating the respective tooth head 25 at the end.
- the shortest radial distance B between the end points S and T of the line segment 24 is at least of precisely the same size, when viewed in an axial projection B of the line segment 24 , as half of the maximum length A of the respective tooth 7 in the radial direction when viewed in an axial projection A.
- the contour of the respective tooth 7 is initially described by a run-in contour 26 in the longitudinal section.
- the run-in contour 26 extends radially from the tooth base 27 outward toward the line segment 24 rising progressively over the rotational axis and merges with the line segment 24 at the radially inner end point of the end points S. Radially on the outside, the line segment 24 merges with a run-out contour 28 which extends from the outer end point T to the tooth base 27 .
- the run-out contour 28 runs from the end point T rising degressively over the rotational axis 1 a .
- the run-in contour 26 and the run-out contour 28 each merge at the tooth base side with the hub 1 at a sectional point Y or Z.
- the radial distance C between the radially outer end point T and the radially outermost of the sectional points Y of the axial projection C is at maximum as large as a third of the maximum length A of the respective tooth 7 in the radial direction when viewed in an axial projection A, with the length A of the respective tooth 7 being described by the distance A between the sectional points Y and Z.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
- Mounting Of Bearings Or Others (AREA)
- Adornments (AREA)
- Gears, Cams (AREA)
Abstract
Description
- The invention relates to a collar made from cold plastically shaped material of a hub, with which at least one inner ring of a wheel bearing unit is secured axially in a fixed manner on the hub and in which teeth for engagement in a mating toothing are formed at the end.
- DE 36 36 243 A1 is concerned with such a collar. The wheel bearing unit, generally an angular ball bearing arrangement or angular roller arrangement, is held free of play in a prestressed fashion by means of the collar. The finished collar 3 according to
FIG. 1 is, as illustrated inFIG. 2 a andFIG. 3 , shaped from ahollow end piece 2 which is formed in one piece with ahub 1. When the collar 3 is formed, the material of theend piece 2 is turned-over plastically over theedge 4 of theinner ring 5 radially toward the outside. If the collar 3, as also illustrated inFIG. 2 b, has an end toothing 6 withteeth 7 for engagement in a mating toothing (not illustrated in more detail), theteeth 7 are either also formed when theend piece 2 is placed around to form the collar 3 or theteeth 7 are formed in the finished collar 3 with a separate method step. The mating toothing is formed, for example, on a bell of a cardan shaft. - The collar 3 is shaped with a tool from the
end piece 2. For this purpose, theend piece 2 which is initially essentially hollow-cylindrical, as illustrated inFIG. 3 , is widened in a radial funnel shape and is shaped in the end position according toFIG. 2 b to form the collar 3. The formation of theteeth 7 is problematic. The material of the part 8 of theend piece 2 tapers during the widening and turning-over process and flows radially outward. Therespective tooth 7 is not fully formed toward the outside owing to the uncontrollable flowing away of the material, and the loadbearing component, which is determined in particular by the dimension B, is small. B is a line segment between the points S and T. The component C and A−(B+C) which is not filled in here is small measured in terms of the overall proportion of thetooth 7 over the length A. - Also, a portion of the material under certain circumstances moves toward the inside in an uncontrolled way so that an
annular gap 31 is formed between theinner ring 5 and thehub 1 and has a disadvantageous effect on the fixed seat of theinner ring 5. - Specialists in the field have attempted to prevent this problem by means of a tool, as presented in DE 36 36 243 A1 which prevents the collar from flowing away radially on the outside. However, the process is generally difficult to implement with the necessary quality owing to tolerances in the dimensions of the blank such as the wall thickness and diameter of the end piece.
- During the mounting of the drive element in the wheel hub arrangement, the drive element and the wheel hub center themselves relative to the rotational axis owing to the geometry of the toothing with respect to one another. A high degree of true running on the connection in the driving mode is thus secured. The mounting of the articulated part with respect to the hub is easy owing to the self-centering but it requires a very high axial prestressing force.
- The edges of all the teeth of the end toothing engage with both edges of all the teeth of the mating toothing. The toothings are braced axially by means of one or more screw elements. Torques are transmitted to the wheel hub by the frictional engagement/positive engagement generated by surface pressure.
- The connection of the articulated part to a wheel hub is advantageous in particular if high torques are to be transmitted from the drive to the wheel or, under certain circumstances, also in the reversed torque flow. The possibilities in terms of installation space and thus in terms of the rigidity of the pairs of inner toothings and outer toothings which are generally used are often already exploited to the full so that the end toothing is, compared to the latter, a reliable alternative which provides a saving in terms of installation space. The rigid configuration for transmitting high torques to the wheel can have a disadvantageous effect if, in the case of overloading, a fracture in the wheel hub leads to loss of the vehicle wheel in the most unfavorable case.
- The object of the invention is therefore to provide a collar with whose design the previously mentioned disadvantages are avoided.
- This object is achieved by means of the features of
claim 1 and a further independent claim. The collar is formed from plastically shaped material of the end piece of the hub. The material of the hollow end piece is preferably shaped cold by what is referred to as rolling riveting, a process of widening, bending and stamping, radially outward over the radially inner and axially outer edge of the inner ring. The end piece which is formed in one piece with the hub is, according to the invention, not essentially hollow-cylindrical but rather has an accumulation of material. The accumulation of material is formed at the part of the end piece which protrudes axially beyond the inner edge of the inner ring. Owing to the rotational symmetry of the end piece, the accumulation of material which runs around the rotational axis is generally a bead-shaped thickened portion which is continuous or interrupted in the circumferential direction. - The thickened portion is designed in any desired way and can protrude in both radial directions, that is to say radially outward away from the rotational axis and/or toward the rotational axis. The thickened portion preferably protrudes out of the end piece radially inward in the direction of the rotational axis of the hub before the collar is formed.
- One embodiment of the invention provides for the thickened portion to be formed on a free, axial end of the end piece which projects from the hub.
- As a result of the accumulation of material on the end piece, enough material is available to fill in the cavities for the teeth in the mold when the toothing is molded. The contour of the tooth is significantly better filled in and the loadbearing part is thus significantly increased. Special measures for restricting the radial flow of material are unnecessary.
- The configuration of the individual tooth can be influenced and optimized by the shape and cross section of the thickened portion. There is thus provision for the outer contour of the thickened portion to drop away toward the end side of the end piece in the direction of the rotational axis.
- The contour of the teeth is represented partially as a line segment in respective sections through the collar which extend through the tooth head along the rotational axis, with the line segment delineating the respective tooth head at the end. The line segment describes the straight profile of the tooth head contour in the longitudinal section along the rotational axis.
- The optimum size of the line segment is provided with configurations of the invention. The shortest radial distance between the end points of the line segment is at least of precisely the same size, when viewed in an axial projection of the line segment, as half of the largest of this length of the respective tooth in the radial direction when viewed in an axial projection of the length of the tooth. Such a minimum amount ensures that each individual loadbearing tooth is filled in the axial direction and in the circumferential direction. The contour of the individual loadbearing tooth is initially described by a run-in contour in a longitudinal section along the rotational axis of the hub, with the run-in contour extending radially from the tooth base outward to the line segment rising over the rotational axis. The run-in contour is curved with any desired degree of concavity or convexity or is a chamfer.
- The run-in contour merges with the line segment at the radially inner end point of the end points. The line segment merges at the radially outer end point of the line segment with a run-out contour toward the tooth base, with the run-out contour extending from the end point rising progressively or degressively or linearly or in any other desired way over the rotational axis.
- The run-in contour and the run-out contour each end at the tooth base side at a sectional point at which the tooth merges with the hub. The sectional point is the root of the tooth at which the contour of the individual tooth merges with the solid base of the collar at the apex of the gap with the respective tooth.
- The distance between the radially outer end point at the end of the line segment and the radially outer sectional point of the sectional points is at maximum as large, in the axial projection, as a third of the maximum length of the respective tooth in the radial direction when considered in an axial projection. The length of the respective tooth is described by the distance between the sectional points.
- The teeth are of wedge-shaped design such that the geometric lines of the end toothing meet centrally at a common point on the rotational axis. The geometric lines are the body edges of the tooth excluding any edge radii, chamfers, rounded portions etc.
- A further embodiment of the invention provides for the edges of the teeth of the end toothing which are provided for engagement to be each inclined at an edge angle greater than 20° and less than 30°. The edge angle is half the tooth angle in the case of a symmetrically formed toothing. The edges are inclined with the edge angle with respect to a virtual pitch plane E which starts from the rotational axis.
- Limits are placed on the dimensions and changes in the dimensions of end toothings on wheel bearings for reasons of installation space. The diameter of the reference circle (median circumference of the end toothing about the rotational axis) of the toothing is accordingly generally prescribed within very tight limits. Accordingly, the behavior of the toothing, for example with respect to loads from the drive torques, can hardly be influenced, or cannot be influenced, by changes to the reference circle of the toothing. With the invention, the geometry of the individual teeth of the toothing is influenced by means of the edge angle in such a way that an optimum number of teeth on a predefined circumference can be specified in terms of assembly and in terms of the loads from torques. The edge angle of the effective edges which are in play-free engagement with the mating toothing is preferably 22.5°. As a result of this configuration, the prestressing forces during mounting are kept low owing to the relatively small axial force components in the toothing. The cross section of each individual tooth in the tooth root is configured in such a way that the end toothing transmits high torques in the rated operation but yields at a prescribed fracture torque.
-
FIGS. 1 to 6 show longitudinal sections or details of longitudinal sections along therotational axis 1 a of a wheel bearing arrangement 9 in various modifications of exemplary embodiments of the invention. -
FIGS. 1 , 3, 5 show a wheel bearing arrangement 9 with ahub 1, two rows of rollingbodies 10 and avehicle flange 11. Thehub 1 has aflange 12 for attaching a vehicle wheel (not illustrated) and is mounted by means of the rollingbodies 10 so as to be rotatable about therotational axis 1 a with respect to thevehicle flange 11 which is fixed to the vehicle. Aninner ring 5 sits on thehub 1 and has a row of the rollingbodies 10 running on it. In the illustrations according toFIGS. 4 and 5 , theend piece hub 1 is in the initial position before the rolling riveting. Theinner ring 5 is, as illustrated in an enlarged detail according toFIG. 6 b, held axially on thehub 1 by means of a collar 16 which has been made to protrude from theend pieces hollow end piece edge 4 of theinner ring 5. Furthermore, the angular ball bearing arrangement is prestressed by means of the collar 16. Anend toothing 13 is formed in the collar 16. - The
hollow end pieces edge 4 which is rounded with a radius R. Theend pieces portion edge 4. - The rotationally symmetrical thickened portion 18 (illustrated in
FIG. 4 ) on theend piece 14 has the largest radial dimension X in the center and protrudes radially in the direction of therotational axis 1 a and radially outward from theend piece 14. During the axial shaping of the collar 16 and of theend toothing 13, the material is distributed in both radial directions. - The thickened
portion 19 which is illustrated inFIG. 5 protrudes radially in the direction of therotational axis 1 a and is thickest at the free end of theend piece 15 which points in the axial direction. During the shaping of theend toothing 13, such an accumulation of material is effective in particular in the region C (FIG. 6 ) so that less material flows outward and is thus available to fill in the cavities in theteeth 7 in the region B. - The thickened
portion 20 illustrated inFIG. 6 a protrudes radially in the direction of therotational axis 1 a. Theouter contour 29 of the thickenedportion 20 drops away toward theend side 21 of theend piece 17 in the direction of therotational axis 1 a. Such a configuration of the invention optimizes the flow and the distribution of the material during the shaping process. -
FIGS. 7 a and 7 b show the overall view of a possible configuration of theend toothing 13 in a highly simplified form. Theteeth 7 are adjacent to one another at the circumference about therotational axis 1 a and oriented radially along the length A.FIGS. 7 a and 7 b show how the geometry is described without rounding of theindividual teeth 7, formed in a wedge shape, at the head, base and edge side by radially orientedgeometric lines geometric lines edges 30 is twice the tooth edge angle α and is constant over the entire radial extent of eachindividual tooth 7. - The contour of the
teeth 7 is represented in respective sections, extending through the tooth head 25 along therotational axis 1 a, through the collar 16 as aline segment 24, with theline segment 24 delineating the respective tooth head 25 at the end. The shortest radial distance B between the end points S and T of theline segment 24 is at least of precisely the same size, when viewed in an axial projection B of theline segment 24, as half of the maximum length A of therespective tooth 7 in the radial direction when viewed in an axial projection A. The contour of therespective tooth 7 is initially described by a run-in contour 26 in the longitudinal section. The run-in contour 26 extends radially from thetooth base 27 outward toward theline segment 24 rising progressively over the rotational axis and merges with theline segment 24 at the radially inner end point of the end points S. Radially on the outside, theline segment 24 merges with a run-out contour 28 which extends from the outer end point T to thetooth base 27. The run-out contour 28 runs from the end point T rising degressively over therotational axis 1 a. The run-in contour 26 and the run-out contour 28 each merge at the tooth base side with thehub 1 at a sectional point Y or Z. - The radial distance C between the radially outer end point T and the radially outermost of the sectional points Y of the axial projection C is at maximum as large as a third of the maximum length A of the
respective tooth 7 in the radial direction when viewed in an axial projection A, with the length A of therespective tooth 7 being described by the distance A between the sectional points Y and Z. -
- 1 Hub
- 1 a Rotational axis
- 2 End piece
- 3 Collar
- 4 Edge
- 5 Inner ring
- 6 End toothing
- 7 Tooth
- 8 Part
- 9 Wheel bearing arrangement
- 10 Rolling body
- 11 Vehicle flange
- 12 Flange
- 13 End toothing
- 14 End piece
- 15 End piece
- 16 Collar
- 17 End piece
- 18 Thickened portion
- 19 Thickened portion
- 20 Thickened portion
- 21 Geometric line
- 22 Geometric line
- 23 Geometric line
- 24 Line segment
- 25 Tooth head
- 26 Run-in contour
- 27 Tooth base
- 28 Run-out contour
- 29 Outer contour
- 30 Edge
- 31 Annular gap
Claims (10)
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102005016427A DE102005016427A1 (en) | 2005-04-08 | 2005-04-08 | Bund with frontal teeth for a drivable hub |
DE102005016427 | 2005-04-08 | ||
DE102005016427.7 | 2005-04-08 | ||
PCT/DE2006/000411 WO2006105748A1 (en) | 2005-04-08 | 2006-03-09 | Collar having end-side teeth for a drivable wheel hub |
Publications (2)
Publication Number | Publication Date |
---|---|
US20080148893A1 true US20080148893A1 (en) | 2008-06-26 |
US7857520B2 US7857520B2 (en) | 2010-12-28 |
Family
ID=36648359
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/910,803 Active 2027-09-18 US7857520B2 (en) | 2005-04-08 | 2006-03-09 | Collar having end-side teeth for a drivable wheel hub |
Country Status (8)
Country | Link |
---|---|
US (1) | US7857520B2 (en) |
EP (1) | EP1866553B1 (en) |
JP (1) | JP2008536075A (en) |
KR (1) | KR101336437B1 (en) |
CN (1) | CN100567748C (en) |
BR (1) | BRPI0607878B1 (en) |
DE (1) | DE102005016427A1 (en) |
WO (1) | WO2006105748A1 (en) |
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US8826542B2 (en) | 2009-05-28 | 2014-09-09 | Schaeffler Technologies Gmbh & Co. Kg | Method for forming an end-side toothing arrangement |
US20100303395A1 (en) * | 2009-05-28 | 2010-12-02 | Schaeffler Technologies Gmbh & Co. Kg | Method for forming an end-side toothing arrangement |
US10072711B2 (en) | 2011-08-10 | 2018-09-11 | Schaeffler Technologies AG & Co. KG | Method for producing a composite rolling bearing |
US9784320B2 (en) | 2011-08-10 | 2017-10-10 | Schaeffler Technologies AG & Co. KG | Method for producing a composite rolling bearing |
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Also Published As
Publication number | Publication date |
---|---|
DE102005016427A1 (en) | 2006-10-12 |
US7857520B2 (en) | 2010-12-28 |
BRPI0607878A8 (en) | 2016-08-30 |
CN100567748C (en) | 2009-12-09 |
KR101336437B1 (en) | 2013-12-04 |
KR20080007572A (en) | 2008-01-22 |
EP1866553A1 (en) | 2007-12-19 |
BRPI0607878A2 (en) | 2009-10-20 |
CN101156000A (en) | 2008-04-02 |
WO2006105748A1 (en) | 2006-10-12 |
BRPI0607878B1 (en) | 2019-02-12 |
EP1866553B1 (en) | 2009-04-29 |
JP2008536075A (en) | 2008-09-04 |
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